EP2756193B1 - Method for monitoring the volumetric efficiency of an hp pump of a hydraulic regulation system for a turbomachine - Google Patents

Method for monitoring the volumetric efficiency of an hp pump of a hydraulic regulation system for a turbomachine Download PDF

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Publication number
EP2756193B1
EP2756193B1 EP12832698.0A EP12832698A EP2756193B1 EP 2756193 B1 EP2756193 B1 EP 2756193B1 EP 12832698 A EP12832698 A EP 12832698A EP 2756193 B1 EP2756193 B1 EP 2756193B1
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EP
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Prior art keywords
turbomachine
pump
valve
engine speed
actuator
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EP12832698.0A
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German (de)
French (fr)
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EP2756193A2 (en
Inventor
Nicolas Potel
Nicolas GOMES
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Safran Aircraft Engines SAS
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SNECMA Services SA
SNECMA SAS
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
    • F02C9/16—Control of working fluid flow
    • F02C9/18—Control of working fluid flow by bleeding, bypassing or acting on variable working fluid interconnections between turbines or compressors or their stages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B51/00—Testing machines, pumps, or pumping installations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/001—Testing thereof; Determination or simulation of flow characteristics; Stall or surge detection, e.g. condition monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/56—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/563—Fluid-guiding means, e.g. diffusers adjustable specially adapted for elastic fluid pumps
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01D—MEASURING NOT SPECIALLY ADAPTED FOR A SPECIFIC VARIABLE; ARRANGEMENTS FOR MEASURING TWO OR MORE VARIABLES NOT COVERED IN A SINGLE OTHER SUBCLASS; TARIFF METERING APPARATUS; MEASURING OR TESTING NOT OTHERWISE PROVIDED FOR
    • G01D5/00—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable
    • G01D5/12—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable using electric or magnetic means
    • G01D5/14—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable using electric or magnetic means influencing the magnitude of a current or voltage
    • G01D5/20—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable using electric or magnetic means influencing the magnitude of a current or voltage by varying inductance, e.g. by a movable armature
    • G01D5/22—Mechanical means for transferring the output of a sensing member; Means for converting the output of a sensing member to another variable where the form or nature of the sensing member does not constrain the means for converting; Transducers not specially adapted for a specific variable using electric or magnetic means influencing the magnitude of a current or voltage by varying inductance, e.g. by a movable armature differentially influencing two coils
    • G01D5/2291—Linear or rotary variable differential transformers (LVDTs/RVDTs) having a single primary coil and two secondary coils
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M15/00—Testing of engines
    • G01M15/14—Testing gas-turbine engines or jet-propulsion engines

Definitions

  • the present invention relates to the general field of gas turbines and more particularly relates to a method for monitoring the volumetric efficiency of the high pressure pump (HP) of the hydraulic control system of a turbomachine without resorting to the use of a sensor or a specific system.
  • HP high pressure pump
  • the field of application of the invention is that of gas turbines for aircraft or helicopter engines which generally comprise a high-pressure volumetric pump for the production of hydraulic energy, the fuel supply of the engines and the lubrication of the various accessories of this engine.
  • the performance of the HP pump is controlled by the high-pressure shut-off valve (HPSOV) which provides the pressurization of the engines and which, knowing the level of leaks in the hydraulic system, makes it possible to determine the level of leakage in the hydraulic system.
  • HPSOV high-pressure shut-off valve
  • the HP pump by removing leaks from various system components such as cylinders, servo drives, and various other intermediate valves.
  • the main object of the present invention is thus to propose a method of monitoring the volumetric efficiency of the HP pump of a turbomachine hydraulic control system that overcomes such drawbacks.
  • said cylinder position is measured by an LVDT sensor of said cylinder and said predetermined flow rate value Q0 corresponds to a calibration threshold of a spring of said valve.
  • the figures 1 and 2 show a simplified block diagram of a turbomachine hydraulic system in two opposite positions of the bypass valve (VBV - variable bypass valve).
  • the high-pressure displacement pump (HP 10 pump) is followed directly downstream by a bypass valve 12 which ensures the pressure rise of the hydraulic system.
  • This valve opens when the flow rate applied to it reaches the precisely known calibration threshold of its spring 12A. It allows on the one hand the setting in motion of a jack 14 ensuring the displacement of the blades with variable geometry (not shown) via an associated servovalve 16 connected by an upstream pipe 18 to the HP pump and by a downstream pipe 20 to the bypass valve 12 and on the other hand the power supply of the motors (not shown) by putting them in communication with the HP pump via successively a fuel metering valve FMV 22 and a high-pressure shut-off valve.
  • pressure HPSOV 24 mounted on a supply line of these engines 26.
  • a computer 28 connected to the various components of the hydraulic system ensures its general control from different data, such as the desired engine speed N or the displacement of the piston 14A of the cylinder 14 measured by a linear variable displacement transducer (LVDT) 14B.
  • LVDT linear variable displacement transducer
  • the hydraulic circuit comprises other known components (for example filters, valves, exchangers, ...) whose description does not appear however necessary for the understanding of the invention and therefore not represented.
  • the operation of the previous system is as follows.
  • the booster of the HP volumetric pump being provided by a BP pump not shown located upstream, this HP pump 10 delivers a flow rate of engine speed N towards the cylinder 14 (via the servovalve 16) and the bypass valve 12.
  • the HP pump naturally leaks on itself and the leakage is even greater as the pump is degraded.
  • the inventors to monitor the volumetric efficiency of the HP pump 10 of the hydraulic control system of a turbomachine, the inventors starting from the observation that if the HP pump degrades over time, the engine speeds N recorded previously will then be different, have developed an innovative process based on the following steps.
  • the engine is in ground operation at a low initial speed N0 and the bypass valve 12 is closed. It is first of all carried out from the computer 28 to the motion control of the actuator 14. However, since the bypass valve is closed, the actuator can not respond. to this command and therefore remains motionless. In parallel with this command, the engine speed N is gradually increased. As the flow sent to the bypass valve 12 is not sufficient, the latter remains closed and the cylinder 14 does not move. When the flow rate is sufficient (determined value Q0 corresponding to the calibration threshold of the spring 12A), the bypass valve 12 opens and the cylinder 14 then starts moving. The engine speed N corresponding to the opening of the bypass valve 12 and thus to the movement of the cylinder is raised by the LVDT 14B of the cylinder to which the computer 28 is connected and stored therein.
  • the curve 50 of the figure 4 which makes it possible to precisely follow the degradation of the efficiency of the HP pump 10 and by defining a limit value N limit not to be exceeded for the engine speed, to then decide on the actions that are necessary in particular as regards the replacement of this HP pump.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • General Physics & Mathematics (AREA)
  • Power Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Control Of Turbines (AREA)
  • Supercharger (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Description

Arrière-plan de l'inventionBackground of the invention

La présente invention se rapporte au domaine général des turbines à gaz et concerne plus particulièrement un procédé permettant une surveillance du rendement volumétrique de la pompe haute pression (HP) du système de régulation hydraulique d'une turbomachine sans recourir à l'utilisation d'un capteur ou d'un système spécifique.The present invention relates to the general field of gas turbines and more particularly relates to a method for monitoring the volumetric efficiency of the high pressure pump (HP) of the hydraulic control system of a turbomachine without resorting to the use of a sensor or a specific system.

Le domaine d'application de l'invention est celui des turbines à gaz pour moteurs d'avions ou d'hélicoptères qui comportent généralement une pompe volumétrique haute-pression pour la production d'énergie hydraulique, l'alimentation en carburant des moteurs et la lubrification des différents accessoires de ce moteur.The field of application of the invention is that of gas turbines for aircraft or helicopter engines which generally comprise a high-pressure volumetric pump for the production of hydraulic energy, the fuel supply of the engines and the lubrication of the various accessories of this engine.

De façon connue en soi (par exemple FR 2 923 871 ), le contrôle du rendement de la pompe HP est réalisé par la vanne de coupure haute-pression (HPSOV - high pressure shut-off valve) qui assure la pressurisation des moteurs et qui connaissant le niveau de fuites du système hydraulique permet de déterminer celui de la pompe HP en y soustrayant les fuites provenant de différents composants du système comme les vérins, les servovannes et divers autres vannes intermédiaires.In a manner known per se (for example FR 2 923 871 ), the performance of the HP pump is controlled by the high-pressure shut-off valve (HPSOV) which provides the pressurization of the engines and which, knowing the level of leaks in the hydraulic system, makes it possible to determine the level of leakage in the hydraulic system. the HP pump by removing leaks from various system components such as cylinders, servo drives, and various other intermediate valves.

Toutefois, si cette solution est pleinement satisfaisante pour l'évaluation des fuites globales du système, elle ne permet pas un suivi précis du rendement de la pompe HP du fait de la dégradation avec le temps de l'ensemble des composants du système et de l'absence de coupure à bas régime de la commande hydraulique des aubes à géométrie variable, ce qui pose un problème lorsqu'il s'agit d'évaluer la capacité de ce système à assurer le redémarrage en vol des moteurs ou lorsqu'il s'agit de planifier, sans impact opérationnel majeur, une dépose de la pompe HP.However, while this solution is fully satisfactory for the evaluation of overall system leaks, it does not allow accurate monitoring of the performance of the HP pump due to the degradation over time of all system components and the system. the absence of low-speed cut-off of the hydraulic control of the blades with variable geometry, which poses a problem when it comes to evaluating the capacity of this system to ensure the restarting of the engines in flight or when it is is to plan, without major operational impact, a removal of the HP pump.

Objet et résumé de l'inventionObject and summary of the invention

La présente invention a donc pour but principal de proposer un procédé de suivi du rendement volumétrique de la pompe HP d'un système de régulation hydraulique de turbomachine qui permette de pallier de tels inconvénients.The main object of the present invention is thus to propose a method of monitoring the volumetric efficiency of the HP pump of a turbomachine hydraulic control system that overcomes such drawbacks.

Ce but est atteint grâce à un procédé de suivi du rendement volumétrique d'une pompe haute-pression d'un système de régulation hydraulique d'une turbomachine comportant une pompe volumétrique haute-pression délivrant un débit Q, fonction d'un régime moteur N de ladite turbomachine défini par un calculateur de commande, en direction d'un vérin d'actionnement des aubes à géométrie variable de ladite turbomachine et d'une vanne de by-pass disposée dans une canalisation d'alimentation des moteurs de ladite turbomachine, caractérisé en ce qu'il comporte les étapes suivantes :

  • mettre en route les moteurs de ladite turbomachine à un bas régime moteur N0, ladite vanne étant fermée,
  • commander depuis ledit calculateur un déplacement dudit vérin,
  • augmenter progressivement ledit régime moteur N jusqu'à ce que ledit débit Q atteigne une valeur prédéterminée Q0 suffisante pour ouvrir ladite vanne,
  • stocker dans ledit calculateur d'une part la position dudit vérin et d'autre part le régime moteur N correspondant à l'ouverture de ladite vanne,
  • répéter les étapes précédentes à des instants t1, t2, tn successifs durant la durée de vie desdits moteurs de la turbomachine, et
  • remplacer ladite pompe volumétrique haute pression lorsque ledit régime moteur N excède une valeur prédéterminée Nlimite.
This object is achieved by means of a method for monitoring the volumetric efficiency of a high-pressure pump of a hydraulic control system of a turbomachine comprising a high-pressure positive displacement pump delivering a flow rate Q, which is a function of an engine speed N said turbomachine defined by a control computer, in the direction of an actuating cylinder of the blades with variable geometry of said turbomachine and a bypass valve arranged in a supply line of the engines of said turbomachine, characterized in that it comprises the following steps:
  • starting the engines of said turbomachine at a low engine speed N0, said valve being closed,
  • controlling from said calculator a displacement of said jack,
  • progressively increasing said engine speed N until said flow Q reaches a predetermined value Q0 sufficient to open said valve,
  • storing in said computer on the one hand the position of said cylinder and on the other hand the engine speed N corresponding to the opening of said valve,
  • repeating the preceding steps at successive times t1, t2, tn during the lifetime of said engines of the turbomachine, and
  • replacing said high pressure displacement pump when said engine speed N exceeds a predetermined value N limit .

Ainsi, en supprimant tout intermédiaire entre la pompe HP et la vanne surveillée, on peut suivre au plus près la dégradation du rendement de la pompe HP et donc aussi surveiller les capacités de redémarrage en vol des moteurs de la turbomachine.Thus, by eliminating any intermediary between the HP pump and the monitored valve, it is possible to closely monitor the degradation of the efficiency of the HP pump and thus also monitor the restart capabilities in flight of the engines of the turbomachine.

De préférence, ladite position du vérin est mesurée par un capteur LVDT dudit vérin et ladite valeur prédéterminée Q0 de débit correspond à un seuil de tarage d'un ressort de ladite vanne.Preferably, said cylinder position is measured by an LVDT sensor of said cylinder and said predetermined flow rate value Q0 corresponds to a calibration threshold of a spring of said valve.

Brève description des dessinsBrief description of the drawings

D'autres caractéristiques et avantages de la présente invention ressortiront de la description faite ci-dessous, en référence aux dessins annexés qui en illustrent un exemple de réalisation dépourvu de tout caractère limitatif. Sur les figures :

  • la figure 1 est un schéma de principe simplifié d'un système hydraulique de turbomachine, vanne de by-pass fermée ;
  • la figure 2 est un schéma de principe simplifié d'un système hydraulique de turbomachine, vanne de by-pass ouverte ;
  • la figure 3 sont deux courbes illustrant respectivement la position vérin et le régime moteur en fonction du temps pendant un démarrage moteur; et
  • la figure 4 est une courbe montrant le régime d'ouverture de la vanne de by-pass en fonction du temps.
Other features and advantages of the present invention will become apparent from the description given below, with reference to the drawings annexed which illustrate an embodiment without any limiting character. In the figures:
  • the figure 1 is a simplified block diagram of a turbomachine hydraulic system, closed bypass valve;
  • the figure 2 is a simplified block diagram of a turbomachine hydraulic system, open bypass valve;
  • the figure 3 are two curves respectively illustrating the cylinder position and engine speed as a function of time during engine start; and
  • the figure 4 is a curve showing the rate of opening of the bypass valve as a function of time.

Description détaillée d'un mode de réalisationDetailed description of an embodiment

Les figures 1 et 2 montrent un schéma de principe simplifié d'un système hydraulique de turbomachine dans deux positions opposées de la vanne de by-pass (VBV - variable by-pass valve).The figures 1 and 2 show a simplified block diagram of a turbomachine hydraulic system in two opposite positions of the bypass valve (VBV - variable bypass valve).

Classiquement, la pompe volumétrique haute-pression (pompe HP 10) est suivie directement en aval par une vanne de by-pass 12 qui permet d'assurer la montée en pression du système hydraulique. Cette vanne s'ouvre lorsque le débit qui lui est appliqué permet d'atteindre le seuil de tarage précisément connu de son ressort 12A. Elle permet d'une part la mise en mouvement d'un vérin 14 assurant le déplacement des aubes à géométrie variable (non représentées) via une servovalve associée 16 reliée par une canalisation amont 18 à la pompe HP et par une canalisation aval 20 à la vanne de by-pass 12 et d'autre part l'alimentation des moteurs (non représentés) par la mise en communication de ceux-ci avec la pompe HP via successivement une vanne de dosage de carburant FMV 22 et une vanne de coupure haute-pression HPSOV 24 montées sur une canalisation d'alimentation de ces moteurs 26. Un calculateur 28 relié aux différents composants du système hydraulique assure son contrôle général à partir de différentes données, comme le régime moteur N souhaité ou le déplacement du piston 14A du vérin 14 mesuré par un capteur LVDT (linear variable displacement transducer 14B). Bien entendu, le circuit hydraulique comporte d'autres composants connus (par exemple des filtres, vannes, échangeurs,...) dont la description n'apparait toutefois pas nécessaire pour la compréhension de l'invention et qui ne sont donc pas représentés. On notera cependant la canalisation 30 de recirculation du débit de la vanne de by-pass reliée à la canalisation aval 20 au travers de la vanne de by-pass 12.Conventionally, the high-pressure displacement pump (HP 10 pump) is followed directly downstream by a bypass valve 12 which ensures the pressure rise of the hydraulic system. This valve opens when the flow rate applied to it reaches the precisely known calibration threshold of its spring 12A. It allows on the one hand the setting in motion of a jack 14 ensuring the displacement of the blades with variable geometry (not shown) via an associated servovalve 16 connected by an upstream pipe 18 to the HP pump and by a downstream pipe 20 to the bypass valve 12 and on the other hand the power supply of the motors (not shown) by putting them in communication with the HP pump via successively a fuel metering valve FMV 22 and a high-pressure shut-off valve. pressure HPSOV 24 mounted on a supply line of these engines 26. A computer 28 connected to the various components of the hydraulic system ensures its general control from different data, such as the desired engine speed N or the displacement of the piston 14A of the cylinder 14 measured by a linear variable displacement transducer (LVDT) 14B. Of course, the hydraulic circuit comprises other known components (for example filters, valves, exchangers, ...) whose description does not appear however necessary for the understanding of the invention and therefore not represented. Note, however, the pipe 30 of recirculation of the flow of the bypass valve connected to the downstream pipe 20 through the bypass valve 12.

Le fonctionnement du système précédent est le suivant. Le gavage de la pompe volumétrique HP étant assuré par une pompe BP non représentée située en amont, cette pompe HP 10 délivre un débit fonction du régime moteur N en direction du vérin 14 (via la servovalve 16) et de la vanne de by-pass 12. La pompe HP fuit naturellement sur elle-même et les fuites sont d'autant plus grandes que la pompe est dégradée.The operation of the previous system is as follows. The booster of the HP volumetric pump being provided by a BP pump not shown located upstream, this HP pump 10 delivers a flow rate of engine speed N towards the cylinder 14 (via the servovalve 16) and the bypass valve 12. The HP pump naturally leaks on itself and the leakage is even greater as the pump is degraded.

Lorsque la vanne de by-pass 12 est dans un état fermé (figure 1), la canalisation 20 entre la sortie de la servovalve 16 et la vanne de by-pass 12 est obstruée par cette dernière. Le delta de pression aux bornes du vérin 14 est nul et les deux chambres de ce vérin étant à pression identique, le piston 14A est immobile ainsi que les aubes à géométrie variable qu'il actionne.When the bypass valve 12 is in a closed state ( figure 1 ), the pipe 20 between the output of the servovalve 16 and the bypass valve 12 is obstructed by the latter. The delta pressure at the terminals of the cylinder 14 is zero and the two chambers of this jack being at identical pressure, the piston 14A is stationary as well as the vanes with variable geometry that it actuates.

Dès que la pression au niveau de la vanne de by-pass 12 dépasse le seuil de tarage du ressort 12A, c'est-à-dire quand le débit qu'elle voit est suffisamment élevé, elle commute dans un état de pleine ouverture (figure 2) et la canalisation 20 entre la sortie de la servovalve 16 et la vanne de by-pass 12 n'est plus obstruée. Le carburant est alors à basse pression et le piston 14A est soumis à une pression différentielle (delta pression non nul) qui le met en mouvement, comme l'illustre la courbe 40 de la figure 3. Le vérin étant équipé du LVDT 14B, il est alors possible au moyen du calculateur 28 de détecter précisément l'instant où le piston est déplacé, correspondant donc à cette ouverture de la vanne de by-pass, et de relever le régime moteur N associé (voir la courbe 42).As soon as the pressure at the bypass valve 12 exceeds the setting threshold of the spring 12A, that is to say when the flow rate it sees is sufficiently high, it switches to a fully open state ( figure 2 ) and the pipe 20 between the output of the servovalve 16 and the bypass valve 12 is no longer obstructed. The fuel is then at low pressure and the piston 14A is subjected to a differential pressure (delta non-zero pressure) which sets it in motion, as illustrated by the curve 40 of the figure 3 . The cylinder being equipped with the LVDT 14B, it is then possible by means of the computer 28 to accurately detect the moment when the piston is moved, corresponding to this opening of the bypass valve, and to raise the associated engine speed N (see curve 42).

Selon l'invention, pour assurer le suivi du rendement volumétrique de la pompe HP 10 du système de régulation hydraulique d'une turbomachine, les inventeurs partant du constat que si la pompe HP se dégrade au cours du temps, les régimes moteurs N relevés précédemment seront alors également différents, ont mis au point un procédé innovant reposant sur les étapes suivantes.According to the invention, to monitor the volumetric efficiency of the HP pump 10 of the hydraulic control system of a turbomachine, the inventors starting from the observation that if the HP pump degrades over time, the engine speeds N recorded previously will then be different, have developed an innovative process based on the following steps.

Le moteur est en fonctionnement au sol à un bas régime initial N0 et la vanne de by-pass 12 est fermée. Il est tout d'abord procédé depuis le calculateur 28 à la commande de mise en mouvement du vérin 14. Toutefois, la vanne de by-pass étant fermée, le vérin ne peut répondre à cette commande et reste donc immobile. En parallèle à cette commande, le régime moteur N est augmenté progressivement. Tant que le débit envoyé sur la vanne de by-pass 12 n'est pas suffisant, cette dernière reste fermée et le vérin 14 ne bouge pas. Quand le débit est suffisant (valeur déterminée Q0 correspondant au seuil de tarage du ressort 12A), la vanne de by-pass 12 s'ouvre et le vérin 14 se met alors en mouvement. Le régime moteur N correspondant à l'ouverture de la vanne de by-pass 12 et donc au mouvement du vérin est relevé grâce au LVDT 14B du vérin auquel le calculateur 28 est relié et stocké dans ce dernier.The engine is in ground operation at a low initial speed N0 and the bypass valve 12 is closed. It is first of all carried out from the computer 28 to the motion control of the actuator 14. However, since the bypass valve is closed, the actuator can not respond. to this command and therefore remains motionless. In parallel with this command, the engine speed N is gradually increased. As the flow sent to the bypass valve 12 is not sufficient, the latter remains closed and the cylinder 14 does not move. When the flow rate is sufficient (determined value Q0 corresponding to the calibration threshold of the spring 12A), the bypass valve 12 opens and the cylinder 14 then starts moving. The engine speed N corresponding to the opening of the bypass valve 12 and thus to the movement of the cylinder is raised by the LVDT 14B of the cylinder to which the computer 28 is connected and stored therein.

En répétant les étapes précédentes à des instants successifs t1, t2, ..., tn au cours de la durée de vie des moteurs, on obtient la courbe 50 de la figure 4 qui permet de suivre précisément la dégradation du rendement de la pompe HP 10 et en définissant une valeur limite Nlimite à ne pas dépasser pour le régime moteur, de décider alors des actions qui s'imposent notamment quant au remplacement de cette pompe HP.By repeating the preceding steps at successive instants t1, t2,..., Tn during the life of the motors, the curve 50 of the figure 4 which makes it possible to precisely follow the degradation of the efficiency of the HP pump 10 and by defining a limit value N limit not to be exceeded for the engine speed, to then decide on the actions that are necessary in particular as regards the replacement of this HP pump.

Claims (3)

  1. A method of tracking the positive displacement efficiency of a high pressure pump in a hydraulic regulator system of a turbomachine having a high pressure positive displacement pump (10) delivering a flow rate Q that is a function of an engine speed N of said turbomachine as defined by a control computer (28), the flow rate Q being delivered to an actuator (14) for actuating variable geometry vanes of said turbomachine and to a bypass valve (12) arranged in a feed pipe (26) for feeding fuel to the engine of said turbomachine, the method being characterized in that it comprises the following steps:
    starting the engine of said turbomachine at a low engine speed NO, said valve (12) being closed;
    using said computer (28) to order a movement of said actuator (14);
    progressively increasing said engine speed N until said flow rate Q reaches a predetermined value Q0 that is sufficient for opening said valve (12);
    storing in said computer (28) firstly the position of said actuator (14) and secondly the engine speed N corresponding to the opening of said valve (12);
    repeating the preceding steps at successive instants t1, t2, tn during the lifetime of said engine of the turbomachine; and
    replacing said high pressure positive displacement pump (10) when said engine speed N exceeds a predetermined value Nlimit.
  2. A tracking method according to claim 1, characterized in that said position of the actuator (14) is measured by an LVDT sensor of said actuator (14).
  3. A tracking method according to claim 1, characterized in that said predetermined value Q0 for the flow rate corresponds to a rated threshold of a spring (12A) of said valve (12).
EP12832698.0A 2011-09-13 2012-08-13 Method for monitoring the volumetric efficiency of an hp pump of a hydraulic regulation system for a turbomachine Active EP2756193B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1158133A FR2979957B1 (en) 2011-09-13 2011-09-13 METHOD FOR MONITORING THE VOLUMETRIC PERFORMANCE OF AN HP PUMP OF A HYDRAULIC TURBOMACHINE REGULATION SYSTEM
PCT/FR2012/051888 WO2013038085A2 (en) 2011-09-13 2012-08-13 Method for monitoring the volumetric efficiency of an hp pump of a turbomachine hydraulic regulation system

Publications (2)

Publication Number Publication Date
EP2756193A2 EP2756193A2 (en) 2014-07-23
EP2756193B1 true EP2756193B1 (en) 2015-11-04

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EP12832698.0A Active EP2756193B1 (en) 2011-09-13 2012-08-13 Method for monitoring the volumetric efficiency of an hp pump of a hydraulic regulation system for a turbomachine

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US (1) US9309882B2 (en)
EP (1) EP2756193B1 (en)
CN (1) CN103917783B (en)
BR (1) BR112014005840B1 (en)
CA (1) CA2848466C (en)
FR (1) FR2979957B1 (en)
RU (1) RU2606465C2 (en)
WO (1) WO2013038085A2 (en)

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* Cited by examiner, † Cited by third party
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FR3009280B1 (en) * 2013-08-02 2017-05-26 Snecma FUEL SYSTEM OF AN AIRCRAFT ENGINE WITH A FUEL RETURN VALVE CONTROLLED BY A PRESSURE DIFFERENTIAL OF A LOW PRESSURE PUMP OF THE FUEL SYSTEM
FR3013837B1 (en) 2013-11-25 2015-12-18 Snecma METHOD FOR TESTING VARIABLE GEOMETRY EQUIPMENTS OF AN AIRCRAFT ENGINE, IN PARTICULAR TURBOMACHINE
CN104696208B (en) * 2015-03-09 2017-03-15 山东科技大学 Mine pump class in-situ check and test method and its loading combination valve
FR3062425B1 (en) * 2017-01-30 2021-01-08 Safran Aircraft Engines TURBOMACHINE FUEL SUPPLY CIRCUIT
CN109538462B (en) * 2018-11-29 2021-01-01 江苏江海润液设备有限公司 Quick start testing method for vertical direct-current pump
CN109869198B (en) * 2019-01-23 2021-06-29 西安热工研究院有限公司 Method for monitoring efficiency of steam turbine full-life high-pressure cylinder based on valve position correction
EP4105120A4 (en) * 2020-03-17 2023-07-26 Sumitomo Precision Products Co., Ltd. Eha system for lifting/lowering landing gear

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GB0007583D0 (en) * 2000-03-30 2000-05-17 Lucas Industries Ltd Method and apparatus for determining the extent of wear of a fuel pump forming part of a fuelling system
FR2818690B1 (en) * 2000-12-22 2003-03-21 Snecma Moteurs TWO-LEVEL PRESSURIZATION VALVE CONTROLLED BY A FUEL DISPENSER
FR2818692B1 (en) * 2000-12-22 2003-08-01 Snecma Moteurs HYDROMECHANICAL MOTOR OVERSPEED LIMITATION SYSTEM
GB0522991D0 (en) * 2005-11-11 2005-12-21 Goodrich Control Sys Ltd Fuel system
GB0525573D0 (en) 2005-12-16 2006-01-25 Rolls Royce Plc Engine Health Monitoring
DE102007044229A1 (en) * 2007-09-17 2009-03-19 Airbus Deutschland Gmbh Aircraft, engine arrangement and engine carrier
FR2923871B1 (en) * 2007-11-19 2013-11-08 Hispano Suiza Sa MONITORING A HIGH PRESSURE PUMP IN A FUEL SUPPLY CIRCUIT OF A TURBOMACHINE.
FR2942001B1 (en) * 2009-02-11 2011-08-26 Snecma SYSTEM FOR MONITORING THE HEALTH STATUS OF EQUIPMENT INVOLVED IN STARTER CAPACITY OF A TURBOREACTOR

Also Published As

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US9309882B2 (en) 2016-04-12
FR2979957A1 (en) 2013-03-15
BR112014005840B1 (en) 2021-07-13
CN103917783A (en) 2014-07-09
CA2848466C (en) 2019-01-22
US20140373611A1 (en) 2014-12-25
CA2848466A1 (en) 2013-03-21
FR2979957B1 (en) 2014-02-14
EP2756193A2 (en) 2014-07-23
CN103917783B (en) 2016-06-01
BR112014005840A2 (en) 2017-03-28
RU2014114523A (en) 2015-10-20
WO2013038085A3 (en) 2014-03-20
WO2013038085A2 (en) 2013-03-21
RU2606465C2 (en) 2017-01-10

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